Spindle bearing device



y 16, 1940- H. H. ROTHSCHILD SPINDLE BEARING DEVICE Filed July 1]., 19382 Sheets-Sheet l s 1 INVENTOR. .at'arr g J1. Qofbschz'ld ATTORNEY.

2 Sheets-Sheet 2 ,JJJ

' H. H. ROTHSCHILD SPINDLE BEARING DEVICE Filed July 11, 1938 July -16,1940.

Xx-m S m v ATTORNEY.

Patented July 16, 1940 SPINDLE BEARING DEVICE Harry H Rothschild, NewYork, N. Y.

' Application July 11, 1938, Serial No. 218,605

3Clairns. (01. 308-154) The p resent invention relates to spindles andmore particularly to hearing devices of spindles for spinning machinesand twister's. The invention contemplates the provision of a spindlebearing in which the spindle proper is substantially free to adjustitself in relation to the center of gravity of the rotating masses underthe influence of the forces acting thereupon. Such a self-adjustingspindle will be practically free from harmful vibrations whichfrequently is no fixed center of gravity of the rotating masses, and thegeometric locus of this center is a certain portion of the spindle axis.The lower end of this portion is defined by the mass and shape of thespindle and the upper end by the shapeymaximum size and weight of thematerial finally spooled on the spindle in addition to the mentionedqualities of the spindle proper.

Now, I have found that in order to minimize vibrations during theoperation of the spindle it is generally sufficient, that the spindle isfree to oscillate-about a point approximately in the middle oftheaforementioned portion of the spindle axis. Even if the point aboutwhich the spindle may oscillate is located nearer the lower end of saidportion of the axis, the vibrations (lo-not exceed admissible limitswith the small spools of conventional size and shape. In consequencethereof, it appears to be permissible for the purposes of my inventionto contemplate a point of said axis portion, if suitably selected inconsideration -of all circumstances, as a fixed center of gravity of therotating masses which does not change its position during the operationof the spindle. Therefore,it is to be understo'od, that'whe'rever I usethe term center of gravity of the rotating masses in 'the specificationhereinafter and in the appended claims, I

wish to denote therewith a suitably selected point between the ends ofsaid portion of theaxis rather than the variable pointwhichwould correspond to a strictly physical definition of the spindle in axial andradial direction are movable onsphe'rica'l surfaces about the center ofgravity of the rotating masses intended to be supported by the device. f

The pulling forces caused by the tensionof the yarns to be spooled onthe spindle do not appear to contribute considerably to the causes ofvibrations in conventional devices, seemingly, because these forcesrotate "uniformly about the spindle axis. The whirl drive, however,exerts a unilateral force upon the spindle, except in th event of aspindle drive by means of an individual electric motor. This force tendsto shift or swing the spindle laterally.

The invention overcomes this drawback by arranging the transverse centerplane of a collar bearing on the same level as the transverse centerplane of the whirl surface engaged by a driving element'such as a band,tape or belt.

Further details and objects of my invention will" be apparent from thedescription hereinafter and'th'e accompanying drawings illustratingseveral embodiments thereof by way of example. "Inthe drawings:

Fig. 1 shows a longitudinal section of an em bodiment of the invention;j

Figs. 2 and 3 are sectional views along line 2-2' and 3-3 respectivelyof Fig. 1;'

Fig. MS a partial development of a part shown I in Fig. '1;

Fig. '5 isa sectional view of a modification;

Fig. 6' is a perspective view of a part of the embodiment I of Fig. 1,and

Fig. Visa longitudinal section of another embodiment. I

In Figs. 1 to 6, a spindle I is shown, to which a whirl 2 is secured byconventional means (not illustrated), the whirl having a pulley surface3. The bearing device for the spindle comprises a substantiallycylindrical .casing 4, having a flange 5, an exteriorly threaded portion6 with a nut 1, and a bottom 8. With the aid of the flange and the nut,the casing 4 may be secured to a machine frame 8' or the like. The topsurface 9 of the casing is spherically shaped, the center of thecurvature being at"), which is a point of the spindle axis, and also ofthe axis of casing 4. A bolster sleeve II is inserted in said casing soas to bear" with its correspondingly shaped ball surface on thespherical surface 9 of the casing. betweensleeve H and the inner wall ofthe casing '4 to permit oscillating movements of the sleeve within thecasing as will be described hereinafter. The upper portion of thebolster Sufiicient clearance is provided at 12 sleeve which protrudesfrom said spherical surface 9 is recessed at l3 and contains the collarbearing M. A nut I4 is screwed into the topmost threaded portion to holdthe bushing or bearing M in position. Instead of the bushing M, ananti-friction bearing 35 may be used as indicated in the modification ofFig. 5. The lower portion of sleeve H has a circular groove l5substantially in registry with an interior peripheral groove I6 ofcasing 4. The lower surface I? of groove I5 is concave andsphericallyshaped having its center in the aforementioned point It. Groove It has aroof shaped cross-section as clearly shown in Fig. l. A ring I8 is inengagement with both the grooves l5 and IS. The

ring illustrated on a larger scale in Fig. 6, con

sists of a resilient material and is slitted at It. The lower ringsurface 20 of the ring corresponds in shape to the spherical groovesurface l1, and its outer surface is wedge-shaped at 2| corresponding tothe inclination of the roof-shaped cross-section of groove IS. The ringmay be recessed at 22 whereby the springing force may be adapted to therequirements. In order to assemble the holster sleeve I I, ring 18 isfirst slipped over the lower end of the sleeve which is tapered at 23for this purpose until it springs into groove 55. Then, the bolstersleeve ll will be inserted into the casing G from its top, whereby ringit will be compressed sufiiciently to pass the upper casing portionuntil it springs also into groove 56. It goes without saying that theouter diameter of the entirely compressed ring must not be greater thanthe inner diameter of the casing, and its inner diameter, whencompressed must not be smaller than the smallest diameter of groove 15.When the ring is in position, it expands. In consequence thereof, itwill be forced downward by the action ofthe roof or wedgeshaped surfaceof groove it in engagement with ring surface 2|, and ring surface 20will be pressed downward on groove surface H. In consequence thereof,bolster sleeve ll will also be pressed upon surface 9 and prevented fromrising, while it is simultaneously free to slide on both surfaces 9 andII, that means to oscillate about the center It. By a forceful pull,however, exerted at the top of the bolster sleeve the latter may beremoved owing to the compressibility of the ring under the action of thesaid wedge-shaped surfaces. Oil conduits 24 may be provided to permitcirculation of oil from the interior to the exterior of the sleeve.

The inner surface 25 of the bottom of the casing is also sphericallyshaped with the center it. On this surface rests a foot step bearing 25having a correspondingly shaped lower surface. Body 26 is cylindricaland substantially narrower than the inner space of the casing so as tobe able to slide laterally, i. e. radially on surface 25. It has asuitably shaped axial recess 27 to receive the foot step of spindle I.An oil conduit 29 is provided in its wall which, at its upper end, hasan inwardly projecting rim 30. This rim permits the removal of the footstep bearing with the aid of a tool applied from the top of the casing 4and hooked under the rim. A resilient meansis provided to exert a slightcentering force upon body 26 so as to hold it in axial position. Saidresilient means consists of a tubular member 3! which encloses the upperportion of body 26 and is secured thereto against rotation by a tongue32'. Tongue 32' is pressed out of the material of member 3! and engagesa recess or indentation 33 of body 26. As apparent from the developmentshown in Fig. 4, member 3! is slitted in its lower portion so as to forma plurality of strips 32. These strips are bent outwardly and bearresiliently against the inner wall of the casing 4. The casing 4 has alongitudinal groove 34 engaged by one of the strips. as clearly shown inFig. 1 and in Fig. 3. Thus, foot step bearing 26 is prevented fromrotation but is free to yield in any radial direction to a forcesufiicient to overcome the slight resistance of the pertaining strip orstrips 32.

The repeatedly mentioned point I0 is so selected that it corresponds tothe definition given lateral force applied in this plane will thus betaken up by the bearing without tending to tilt the spindle in thelatter. importance if bearing M is an anti-friction bearing comprisingballs, needles or rollers. Furthermore, it is advisable to arrange thespherical supporting surface 9 as close as possible to the hearing italthough, in many instances, the small dimensions of the whirl will notpermit to comply with the suggestion. The distance of the This is ofparticular.

spherical surface I? from surface 9 should be between one-fourth toone-half of the distance of spherical surface 25 from surface 9 in viewof conventional spindle. dimensions. The separation of the foot stepbearing 26 from the bolster sleeve H, or in other words, the shortnessof sleeve H offers two important advantages: first,

the oil capacity of the casing is unusually great in comparison toconventional casings of the same diameter, and second, the masses to bemoved when. the spindle tends to adjust its position are smaller than inthe case of a sleeve comprising the collar bearing and the foot stepbearing.

The clearance between the outer wall of. body 26 and the inner surfaceof the resilient j strips 32 should be not less than of an inch g forspindles of the size mostly in use.

Now it is apparent that the spindle isv free to oscillate about theselected center point H! since the sleeve H as well as the foot stepbearing 25 can readily follow such movement on their spherical surfaces9, l1 and 25 respectively. Consequently, the spindle will adjust itselfin the position best suited under the prevailing forces. The resilientmember 3| exerts only a slight correcting force tending to establish thevertical position of the axis. Owing to the se iection of the center ofoscillations in the center of gravity of the rotating masses thevibrations of the spindle are minimized. 1

In certain instances, it is desirable that the spindle can be adjustedas to its height within certain limits. Means may be provided, there-'fore, to alter the distance of the foot step bearing from the collarbearing.

In this figure, the casing I04 is open at its lower In the embodiment of'7, an'example of such means is illustrated.

end. which is interiorly threaded at I45. A screw with head Hi4 engagesthe threads I45 and carfor the foot step bearing member I26. The memberI43 has a spherical upper surface with its center at III). By turningscrew I44 the supporting member I43, and, thus, foot step bearing memberI26 may be raised or lowered. It is self-evident that screw I44 andmember I43 may be made of one piece if this is preferred. Furthermore,it is advisable to fit member I43 tightly like a piston in the casingI04 in order to ensure its axial position. A gasket I46 and a check nutI4I are provided, the one to prevent oil from escaping, the other one tosecure the adjusted position. The structure offers the additionaladvantage that the casing may be opened from below to remove sump oil.It will be noticed that the radius of the curvature of surface I canonly be correct for one position of the member I43 with respect to thecenter IIO. Owing to the fact that the distance of I25 to H0 isrelatively great and that the range of adjustability of member I43 isonly small, the occurring incorrectness is admissible. In order tofacilitate the sliding of member I26 on surface I25 in every position, Iprefer to curve surface I25 with a radius taken from point III). to thelowest active position of member I43 and to curve the bottom surface ofmember I26 with a radius taken from point IIO to the highest activeposition of member I43.

In bearing devices for very heavy spindles such as bucket spindles, thetapered foot step illustrated in Fig. 1 is not applicable. Fig '7 showsa modified form of the foot step bearing which is suited to carryheavier loads. For this purpose body I20 is so designed as to be fittedwith a foot step bearing and a collar hearing. The recess I21 of memberI26 is cylindrical as is also the foot step I28 of spindle IDI. Ananti-friction foot step bearing I42 is provided at the bottom of therecess, and a collar bearing I4I near its top. The collar bearing may bea bushing, or a ball bearing as shown or it may be a needle bearingwhile a ball bearing I42 at the bottom of the recess is preferred.

The embodiment of Fig. 7 shows also a modifled whirl I02 of a form asfrequently used in the spinning of silk and rayon threads. The very highcenter of gravity III] of the rotating masses and the height andnarrowness of the whirl causes the arrangement of the spherical surfaceI09 on a lower level than suggested in the rule given hereinbefore.However, owing to the peculiarity of the drive in devices of this type,the unilateral force is usually smaller than that acting on spindles asshown in Fig. 1. Furthermore, the greater width of the belt engaging awhirl of the type I02 has a steadying effect on the spindle. Inconsequence thereof, the greater distance of surface I09 from collarbearing II4 will not be harmful.

Although I have described several embodiments of my invention I do notwish to limit myself to structure, and many alterations andmodifications of the shape and combination of parts within the scope andspirit of my invenical surface for engagement with said concave.

surface of said bolster sleeve, and being held substantially in apre-determined position relatively to said casing, all said sphericalsurfaces substantially having a common center.

2. In a spindle bearing device, a casing, a bolster sleeve, a securingmeans for said bolster sleeve, and a foot step, said bolster sleevehaving an upper convex and a lower concave spherical surface, said footstep having a lower convex surface, said casing having two concavespher-' ical surfaces for engagement with said convex surfaces of saidbolster sleeve and said foot step respectively, said securing meanshaving a convex spherical surface for engagement with said concavesurface of said bolster sleeve, and being held substantially in apre-determined position relatively to said casing, all said sphericalsurfaces substantially having a common center near the center of gravityof the rotating masses intended to be supported by said device.

3. In a device of the type described, a casing,

